Servomotor actuating means



March 16, 1965 H. B. SCHULTZ SERVOMOTOR ACTUATING MEANS Original Filed Aug. 2, 1961 3 Sheets-Sheet l INVENTOR. HAROLD B. SCHULTZ March 16, 1965 H. B. SCHULTZ SERVOMOTOR ACTUATING MEANS 3 Sheets-Sheet 2 Original Filed Aug. 2, 1961 m lfill INVENTOR. #15010 a. sum 72.

March 16, 1965 H. B. SCHULTZ SERVOMOTOR ACTUATING MEANS 3 Sheets-Sheet Original Filed Aug. 2, 1961 IIIIII: llllllc mm M INVENTOR. HAROLD B. $CHULTZ MAM A TTO/QNEY.

United States Patent Ofilice 2 Claims. (Cl. 91-369) The present invention relates to actuating means for servomotors of the type carrying control structure on its movable power driven elements; and more particularly to actuating structures for the type of servomotor driven hydraulic master cylinders used to power actuate the hydraulic brakes of automotive vehicles. This application is a division of my copending application Serial No. 128,- 720 filed August 2, 1961.

The fluid pressure servomotorswhich are used to power actuate the hydraulic brakes of automotive vehicles generally include a control valve structure mounted on the power piston of the servomotor--which control valve is in turn actuated by means of a foot pedal lever. It is a property of the brake structures of the drum and shoe type, that a considerable amount of brake pedal lever movement is required to force the shoes out into engagement with the drums, and thereafter only a slight additional amount of foot pedal lever movement is required to produce the actual braking force. The brake operation therefore may be thought of as occurring in two stages: the first stage of which requires a large amount of fluid at low pressure to move the shoes into engagement with the drums; and the second stage of which requires a small amount of fiow at a high pressure to produce the braking force. In most systems the transition between the stages occurs at a hydraulic pressure of approximately 100 psi. In general, the servomotor driven master cylinders which are used to actuate these systems discharge fluid to the brake structures in an amount generally proportional to the movement of the controlling foot pedal lever. It has long been desired by the art to reduce the amount of foot pedal lever travel required to actuate such mechanisms to an amount which generally corresponds with that required to operate an accelerator pedal of an automotive vehicle.

An object of the present invention is therefore the provision of a new and improved servomoto-r structure controlled by a manually actuated member whose actuation will occur in two stages: the first of which produces a considerable movement of servomotor movement by means of a very small amount of movement of the manually actuated lever; and a second stage wherein the servo-motor movement is generally directly proportional to the movement of the manually actuated member.

A more particular object of the present invention is the provision of a new and improved fluid pressure servomotor driven master cylinder of an automotive braking system wherein the shoes of the brake structures are forced out into engagement with their drums by the servomotor without requiring any substantial movement of the manually actuated member; and thereafter the manually actuated control member is caused to have a movement which is substantially directly proportional to the force applied between the brake and shoes and brake drums.

, A still further object of the present invention is the provision of a new and improved actuating mechanism for servomotors which can be interpositioned between a control structure mounted on the movable member of the servomotor, and a manually actuated control lever and wherein the connection expands during actuation of the servomotor to reduce the amount of followup move- 3,173,333 ?atented Mar. 16, 1965 ment of the servomotors movable elements by the manually actuated control member.

The invention resides in certain constructions and combinations and arrangements of parts; and further objects and advantages will become apparent to those skilled in the art to which the invention relates from the following description of several preferred embodiments described with reference to the accompanying drawings forming a part of this specification, and in which:

FIGURE 1 is a schematic view of an automotive braking system in which its fluid pressure servomotor driven master cylinder and actuating mechanism is shown in section;

FIGURE 2 is a cross-sectional view taken approximately on the line 22 of FIGURE 1;

FIGURE 3 is a fragmentary cross-sectional view showing another embodiment of fluid pressure servomotor and its actuating mechanism; and

FIGURE 4 is a fragmentary enlarged view of the embodiment shown in FIGURE 3.

The automotive braking system shown in FIGURE 1 of the drawings generally comprises a conventional master cylinder A having a fluid pressurizing chamber 10 therein from which hydraulic fluid is forced by reason of the hydraulic piston 12 to the hydraulic motors 14, only one of which is shown, of a conventional drum and shoe type brake B. The piston 12 is adapted to be power driven by means of the movable wall or power piston 16 of a fluid pressure servo-motor C attached to the master cylinder A. The control valve structure D for the servomotor C is mounted on and carried by the movable wall 16 of the servomotor; so that movement of the control rod 18 of the control valve structure D causes the movable wall 16 to move correspondingly. The servomotor C shown in the drawings is of the vacuum submerged type wherein vacuum of the same intensity is normally communicated to the front and rear power chamhers 2t) and 22 on the front and rear sides respectively, of the movable wall 16 during the normal energized condition shown in the drawing.

The control valve D shown in the drawings is of conventional construction and generally comprises a stationary vacuum valve seat 24, a concentric and movable vacuum atmospheric valve seat 26, and an annular poppet member 23 adapted to abut each of the valve seats. The valve structure is contained within an axially extending opening 30 which extends through the movable wall 16 and which is provided with a rearwardly facing step to provide a rearwardly facing shoulder which forms the vacuum valve seat 24. The atmospheric valve seat 26 is formed on the rear end of a movable valve control member 32 that is positioned in the opening 39' generally forwardly of the vacuum valve seat 24!. The control rod 18 which is suitably attached to the control member 32 so as to be an operating part thereof controls the movement of the control member 32.

The annular poppet member 28 is formed of rubber and includes a front flange which is molded onto and around a suitable stiffening plate to effect a suitable seal with respect to both of the valve seats 24 and 26. The rear end of the poppet member 28 is provided with an integral flexible diaphragm portion which is suitably secured to the sidewalls of the opening 3% to effect a seal therewith. The annular area between the poppet member 28 and sidewalls of the opening 3% in the region between the vacuum valve seat 24 and the diaphragm portion 3 1 forms the vacuum chamber 36 of the valve. Vacuum is continually communicated to the vacuum chamber 36 through the vacuum inlet connection 38 to the chamber 29 and .the vacuum passage 41? in the movable wall 16.

The region of the central opening 31 forwardly of the r3 valve seats 24 and 25 forms the control chamber 42 of the valve, and is continually communicated to the rear opposing power chamber 22 by means of the radial passage 44-. The central opening 3t) extends externally of the housing of the servomotor through a tubular boss 46 which is suitably sealed with respect to the housing so that atmospheric pressure is continually communicated through the central opening in the annular poppet member 28 to the atmospheric valve seat 26.

The servomotor driven master cylinder structure above described is shown in FIGURE 1 in its normal deactivated condition wherein vacuum of the same intensity is communicated to both the forward and rearward power chambers 20 and 22 respectively, and no pressure is being supplied to the brake applying wheel cylinders 14. When it is desired to actuate the brakes, the control rod 18 is forced inwardly to cause the poppet member 28 to abut the vacuum valve seat 24 and close oil vacuum communication with the rear opposing power chamber 22. Thereafter a slight further forward movement of control rod 18 moves the atmospheric valve seat 26 out of engagement with the poppet member 28, thereby causing air pressure to flow through the opening 35) to the rear opposing power chamber 22 and force the movable wall 16 forwardly. Movement of the movable wall 16 is transmitted through the push rod 50 to the piston 12 causing it to close off its compensating port 52 and thereafter force fluid to the brake applying wheel cylinders 14. A block of rubber 53 is positioned between the movable wall 16 and push rod 58 to provide a reaction force against the control member 32 which is generally proportional to the force applied to the push rod When it is desired to prevent further increase in braking effort, forward movement of the control rod 18 is stopped; whereupon flow of air through the valve continues for a further instant until the movable wall 16 moves forwardly to allow the poppet member 28 to again engage the atmospheric valve seat 26. Thereafter all flow through the valve structure is stopped and the piston 12 remains in a stationary position. When it is desired to release the brakes, the control rod 18 is allowed to move rearwardly; whereupon the atmospheric valve seat 26 moves the poppet member 28 out of engagement with the vacuum valve seat 24 to communicate vacuum with the rear opposing power chamber 22. The resulting decrease in pressure ditferential across the movable wall 316 permits the hydraulic pressure in the chamber plus the force of the piston return spring 54 to move the movable wall 16 rearwardly. The movable wall 16 will stop in any position in which the control rod 18 is held; and if it is desired to completely release the brakes, the removement of all force from the control rod 18 allows the spring 56 to hold the poppet member 28 out of engagement with the vacuum valve seat 24, so that the structure again assumes the position shown in the drawing. general structure so far described is similar to that shown and described in the Robert R. Hager application 98,472, and for a more complete understanding of its construction and operation reference may be had to that application.

conventionally, control rod portion 18 of the control member32-is actuated through mechanical means that is directly connected to the foot pedal lever 48 of the automotive vehicle on which it is mounted. conventionally therefore the movable Wall 16 is caused to assume a position correspoding with the position to which the foot pedal lever 48 is moved.

As previously indicated it is an object of the present invention to reduce the amount of pedal lever movement that is required to actuate the braking systemparticularly during the time that the brake shoes are moving out of engagement with the brake drum, and during which a relatively large amount of fluid is required to force the shoes into engagement with the drums. This is accomplished in the embodiment shown in FTGURE l, by means of an expansible or telescoping member E having a hydraulic chamber 58 positioned between its movable parts for caus- The ing an extension thereof. The structure E shown in FIG- URE 1 has a body portion 60 having a forwardly facing hydraulic chamber 53 therein which is closed off by means of the hydraulic piston 62. The piston is suitably sealed with respect to the sidewalls of the chamber 58, and the control rod 13 is suitably fixed to the hydraulic piston s2 so that its movement is controlled thereby. The rear end of the body portion 6%) is suitably pinned to the foot pedal lever 48. A suitable guide bearing 64 is interpositioned between the front end of the body portion 6% and control rod 13, so that the telescoping member E is suitably supported between the foot pedal lever 43 and the control member 32 to accommodate a slight amount of lateral movement.

Although the expansible member E may be caused to expand at various times during the actuation of the unit to produce various effects, it is shown in FIGURE 1 as being connected to the output of the fluid pressure chamber 10 of the master cylinder to receive fluid pressure therefrom. As the servomotor C is actuated therefore, gradually increasing pressure from the chamber 10 is communicated to the hydraulic chamber 58 to cause it to expand proportionately so that very little, if any, movement of the control foot pedal lever 43 is necessary. It has been chosen in the embodiment shown in FIGURE 1 to terminate the expansion of the member E at approximately the time that the brake shoes engage the brake drums. This occurs when the pressure in the discharge of the master cylinder A reaches a pressure of approximately 100 p.s.i.; by reason of a valve structure P which closes oil communication between the master cylinder and the expansible chamber 58 at this time. The valve structure F can best be seen in FIGURE 2 of the drawings, and as shown, is formed in the body section 69 by means of a transverse passage or bore 66 beneath the expansiole chamber 58. The bore 66 is provided with an outwardly facing shoulder 68 against which a ball valve 70 is adapted to seat and to shutoff flow from the master cylinder to the expansible chamber 58. Flow from the master cylinder enters the open end of the bore 66, and a small passageway 72 inwardly of the shoulders 68 communicates this flow to the expansible chamber 58. A coil spring 74 is provided to bias the ball 76 toward the valve seat 68, and the ball 70 is normally held out of engagement with the valve seat 68 by means of a hydraulic piston 76 that is positioned inwardly of the valve seat 68. A coil spring 78 biases the piston 76 to a position which holds the ball 70 out of engagement with the valve seat 68. The coil spring 73 works through a washer 80 which abuts a shoulder 82 on the piston member 76, and valve opening movement is limited by abutment of the washer 3b with another shoulder 84 in the opening 66. The spring 73 is normally compressed by an amount which holds the piston 76 in its valve opening position until a pressure of approximately psi. is asserted against the piston; whereupon the force of spring 78 is overcome and the piston moves to allow the ball 72 to abut the valve seat 68. Thereafter further expansion of the telescoping member E is prevented, and the foot pedal lever 48 moves in accord with the power member 16. Inasmuch as this occurs after the time that the brake shoes have engaged the brake drum, there is thereafter provided a movement of the foot pedal lever 48 which is indicative of the amount of braking effort being produced.

The embodiment of brake actuating system shown in FIGURE 3 of the drawings corresponds generally with that shown in FIGURE 1, and differs principally therefrom in the arrangement of expansible member E which is used to actuate the control rod 18'. The structure shown in FIGURE 3 is'intended to actuate a master cylinder A which is identical with that shown in FIGURE 1; and those portions of FIGURE 3 which are similar to corresponding portions in FIGURE 1 are designated by like numeral or letter, characterized further in that a prime mark is afiixed thereto.

The expansible structure E is a hydraulic equivalent of the general structure E shown in FIGURE 1 in that motion from the pedal lever 48 is transmitted to the control rod 18 by means of hydraulic displacement. The structure shown in FIGURE 3 generally comprises a conventional master cylinder 86, which may be identical to the master cylinder A shown in FIGURE 1, and which is actuated by means of the foot pedal lever 48'. In general the structure E includes an expansible chamber 58 which is expanded during the initial stage of brake actuation without using any of the displacement from the master cylinder 86, until such time as the brake shoes engage the drums. Thereafter displacement from the master cylinder 86 is valved to the expansib-le chamber 58 so that movement of the foot pedal lever 48 then occurs in a manner proportional to the amount of braking effort which is achieved. The structure E generally comprises a cast housing 88the forward portion of which is suitably fixed as by snap rings 99 to the movable wall structure 16' of the fluid pressure motor C, and the rear portion of which is provided with an axially extending cylinder bore forming the expansible chamber 58'. A piston 92 closes off the rear end of the expansible chamber 58, and the piston 92 is held stationary by means of a bracket 94 which extends between the piston 92 and the shell of the servomotor structure C. It will therefore be seen that movement of the power piston 16' causes an expansion of the expansible hydraulic chamber 58.

The forward end of the cast housing 38 is also provided with an axially extending valve actuating bore 96 of substantially the same size as is the bore 58. The bore 96 is closed off by means of a piston 98 which is shown at an integral part of the control rod 18. Discharge from the master cylinder 86 is continually communicated to the valve actuating bore 96, so that pressure upon piston 98 causes an actuation of the servomotor C which is directly proportional to the pressure generated in the master cylinder 86.

The structure shown in FIGURE 3 further includes a valve structure F for controlling communication between the expansible chamber 58 and the low pressure reservoir 1% of the master cylinder 86. In the embodiment shown in FIGURE 3, communication is permited up until such time as the pressure generated in the master cylinder 86 causes a pressure to be produced in the outlet of master cylinder A, not shown, of approximately 100 psi. At this time, the valve structure F is actuated to close off communication between the reservoir 1% and expansible chamber 58, and communicates the discharge of the master cylinder 86 to the expansible chamber 58 to provide a follow-up movement of the foot pedal lever 48'.

The valve structure F is formed in the housing 88 by means of a vertical bore 1&2 having an outlet port in its inner end which communicates directly to the expansible chamber 58. Adjacent the inner end of the vertical bore 1&2 there is provided a pressure inlet passage 1&6 which communicates pressure from the master cylinder 86 to the outlet passage 104. The outlet passage 104 is adapted to be closed oif by means of a needle type poppet 108 which is yieldably carried by a piston 11% in the bore 102. The needle type poppet 108 has a cylindrical head 112 thereon which is slidingly received within a bore 114 in the bottom end of the piston 110. Downward movement of the piston 110 is limited by means of engagement of flange 116 on the piston 110 with a shoulder 11%, and the piston is normally held in this position by means of a coil spring 120. A predetermined sealing force is provided for the poppet 108 by a coil spring 122 positioned between the poppet 108 and the bottom of the bore 114 and separation of the needle poppet 1418 from the piston 11%) is prevented by suitable snap ring means in the bore 114 beneath the cylindrical head 112 of the poppet 108.

The upper end of the piston 110 is provided with a tubular projecting portion 124, and the outer end of the bore 192 is closed off by a cap 126 having a bore 128 6 W which slidingly receives the outer end of the tubular projection 124, and which bore 128 is always communicated to the expansible chamber 58'. The space 131) between the cap 126 and piston 11% is always communicated with the reservoir 1% by means of line 131. A drilled passage 132 through the tubular projection 124 is provided for communicating chamber 13-0 with the central opening 133 through the tubular projection 124. The cap member 126 further includes a stepped bore 134 com municating with bore 128 and having needle type poppet 135 therein which is yieldably biased into chamber 128 to a position spaced from the end of the tubular projection 124 when the flange 116 engages the shoulder 118. Upward movement of the tubular portion 124 causes it to abut the end of the needle poppet 135 to close oif flow through the tubular projection 124. The portion of the bore 128 in the cap member 126 into which the tubular member 124 projects is communicated by means of a passage 136 to bore 134 and its passage 137 in the cast housing 33 leading to the expansible chamber 58.

During the normal de-energized condition of the system therefore, the piston 11d engages the shoulder 118, passage 104 is closed off by the poppet 163, and the poppet 135 is out of engagement with the tubular projection 124 to permit flow of fluid from the reservoir 109' to the expansible chamber 58. Depressing of the foot pedal lever 48 builds up pressure within the master cylinder 86 which causes the piston 98 to move the control rod 18 and hence actuate the servomotor C to force fluid out of its actuated master cylinder A, not shown. Movement of the movable wail 16 of the servomotor C causes the housing 88 to move along with it; and inasmuch as the piston 92 is held stationary with respect to the housing of the servomotor C by means of a suitable bracket 94, the expansible chamber 58 is caused to enlarge. Inasmuch as the poppet 135 is out of engagement with the tubular portion 124, low pressure fluid from the reservoir 1% is free to enter the expansible chamber 58' as it is expanded by the movable wall 16. The only displacement therefore which is used from the master cylinder 36 during this initial stage of actuation, is that required to actuate the control valve structure D, and therefore substantially no movement of the foot pedal lever 48 takes place.

After a predetermined pressure has been developed by the master cylinder 86, the spring 12% yields to allow the piston to move upwardly to sequentially close off the passage 137 through the tubular projection 124 from the expansible chamber 53, and thereafter lift the poppet 168 out of sealing engagement with the seat surrounding passage 104, to communicate fluid discharge from the master cylinder 36 to the expansible chamber 58. Thereafter any further actuation of the foot pedal lever 48 causes displacement of the master cylinder 86 to be used to enlarge the cxpansible chamber 58 so that there would be a movement of the foot pedal lever 48' generally corresponding to that of the movable wall 16' of the servomotor C. In the preferred embodiment shown in the drawing, the spring 129 is preloaded to yield when the pressure from the master cylinder 86 produces a suificient actuation of the servomotor C to cause the shoes of the vehicles brakes to engage their brake drums.

It will be apparent that the valve structure F can be modified to cause different arrangements of follow-up movement of the movable wall 16 by the foot pedal lever 43. Where for example, the valve structure F is made to communicate the master cylinder 8-5 to the expansible chamber 53' normally, and at a predetermined pressure close off communication between the expansible chamber 58 and the master cylinder 86, and in tum communicate it with the reservoir 1%; foot pedal lever movement would be provided initially, and would thereafter be prevented from exceeding a predetermined value. This arrangement can be used to provide brake operation at the time that the brake pedal lever would normally be bottomed out against the floor boards of the vehicle.

It will be apparent that the objects heretofore enumerated, as well as others, have been accomplished, and that there has been provided an actuating system for a servomotor of the follow-up type which prevents follow-up movement of the manually actuated lever during certain periods of actuation.

While the invention has been described in considerable detail, I do not wish to be limited to the particular construction shown and described; and it is my intention to cover hereby all novel adaptations, modifications and arrangements thereof which come within the practice of those skilled in the art to which the invention relates.

I claim:

1. In an actuating system for a servomotor having a power driven movable structure on which a control member for the servomotor is mounted in such manner that movement of said control member in one direction causes said power driven structure to move in said direction and thereby cause the control member to follow the actuating movement of said power driven structure: a support, telescopic means operatively connected between said power driven structure and said support, said telescopic means having telescoping parts forming an expansible hydraulic chamber which is expanded during movement of said power driven member in said one direction, primary means for developing a primary hydraulic pressure signal, pressure responsive means communicating with said primary means and connected to said control member for actuating said control member in said one direction, a reservoir of hydraulic fluid, flow communicating means for communicating said reservoir to said expansible chamber, and valve structure for closing off said flow communicating means and thereafter communicating said primary means to said expansible chamber.

2. In an actuating system for a servomotor having a power driven movable structure on which a control memher for the servomotor is mounted in such manner that movement of said control member in one direction causes said power driven structure to move in said direction and thereby cause the control member to follow the actuating movement of said power driven structure: a support, telescopic means operatively connected between said power driven structure and said support, said telescopic means having telescoping parts forming an expansible hydraulic chamber which is expanded during movement of said power driven member in said one direction, primary means for developing a primary hydraulic pressure signal, pressureresponsive means communicating with said primary means and connected to said control member for actuating said control member in said one direction, a reservoir of hydraulic fluid, flow communicating means for communicating said reservoir to said expansible chamber, and valve structure for closing off said flow communicating means and thereafter communicating said primary means to said expansible chamber, said valve structure-being actuated by the pressure developed in said primary means.

References Cited in the file of this patent UNITED STATES PATENTS 2,275,697 Stelzer Mar. 10, 1942 2,525,426 Rockwell Oct. 10, 1950 2,646,665 Rockwell July 28, 1953 2,847,828 Porter Aug. 19, 1958 2,924,072 Burwell Feb. 19, 1960 

1. IN AN ACTUATING SYSTEM FOR A SERVOMOTOR HAVING A POWER DRIVEN MOVABLE STRUCTURE ON WHICH A CONTROL MEMBER FOR THE SERVOMOTOR IS MOUNTED IN SUCH MANNER THAT MOVEMENT OF SAID CONTROL MEMBER IN ONE DIRECTION CAUSES SAID POWER DRIVEN STRUCTURE TO MOVE IN SAID DIRECTION AND THEREBY CAUSE THE CONTROL MEMBER TO FOLLOW THE ACTUATING MOVEMENT OF SAID POWER DRIVEN STRUCTURE; A SUPPORT, TELESCOPIC MEANS OPERATIVELY CONNECTED BETWEEN SAID POWER DRIVEN STRUCTURE AND SAID SUPPORT, SAID TELESCOPIC MEANS HAVING TELESCOPING PARTS FORMING AN EXPANSIBLE HYDRAULIC CHAMBER WHICH IS EXPANDED DURING MOVEMENT OF SAID POWER DRIVEN MEMBER IN SAID ONE DIRECTION, PRIMARY MEANS FOR DEVELOPING A PRIMARY HYDRAULIC PRESSURE SIGNAL, PRESSURE RESPONSIVE MEANS COMMUNICATING WITH SAID PRIMARY MEANS AND CONNECTED TO SAID CONTROL MEMBER FOR ACTUATING SAID CONTROL MEMBER IN ONE DIRECTION, A RESERVOIR OF HYDRAULIC FLUID, FLOW COMMUNICATING MEANS FOR COMMUNICATING SAID RESERVOIR TO SAID EXPANSIBLE CHAMBER, AND VALVE STRUCTURE FOR CLOSING OFF SAID FLOW COMMUNICATING MEANS AND THEREAFTER COMMUNICATING SAID PRIMARY MEANS TO SAID EXPANSIBLE CHAMBER. 